CN206957987U - A kind of centrifugal blower volute - Google Patents
A kind of centrifugal blower volute Download PDFInfo
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- CN206957987U CN206957987U CN201720594983.5U CN201720594983U CN206957987U CN 206957987 U CN206957987 U CN 206957987U CN 201720594983 U CN201720594983 U CN 201720594983U CN 206957987 U CN206957987 U CN 206957987U
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Abstract
A kind of centrifugal blower volute, including protecgulum, bonnet and the ring wall being connected between protecgulum and bonnet, the spiral case inlet pressure of the spiral case includes the start line AC and the end lines MN positioned at the molded line other end positioned at molded line one end, and start line AC and end lines MN are adjacent to fan outlet, it is characterised in that：The spiral case inlet pressure also includes the first constant helix CD of the angle of flare and tapered the second helix EM of the angle of flare, first helix CD is connected with start line AC, second helix EM is connected with end lines MN, also, ring wall width before and after the outer side edges of fan outlet is more than the front and rear width of inner side edge.The utility model has the advantage of：Spiral case side-to-side dimensions are transformed into anteroposterior dimension change by the centrifugal blower volute by Transformed area, improve the fluency that spiral case internal gas flow is collected and passed through, larger lifting maximum static pressure and the static pressure of effective wind rate section, realize and are issued to big spiral case effect in small size, lift Consumer's Experience.
Description
Technical field
A kind of blower fan is the utility model is related to, more particularly, to a kind of centrifugal blower volute.
Background technology
Centrifugal blower has obtained extensive reference with the advantages that its suction is big, noise is low, compact-sized in range hood.
Spiral case is one of core component of centrifugal blower, and it is to concentrate the gas for leaving impeller that it, which is acted on, is exported to volute outlet, and will
Dynamic pressure is changed into static pressure.The volute structure of existing centrifugal blower includes spiral case top plate, spiral case bottom plate and connection spiral case top plate, spiral case
Remaining molded line in addition to snail tongue position is consistent with spiral case bottom plate for the spiral case coaming plate of bottom plate, wherein spiral case top plate.Conventional volute design one
As carried out by a metatheory, have two it is assumed that i.e. flow parameter is uniformly distributed and spiral case interior air-flow is moved on hypothesis import circumference
Moment preserving is measured, the spiral case inlet pressure by unitary Theoretical Design is usually equiangular helical spiral.But actually due to the non-axle pair of volute shape
Claim, the particularly influence of snail tongue, can form a pressure field heterogeneous in impeller outlet, impeller outlet, i.e. snail will necessarily be made
Shell inlet flow field is uneven.Due to a metatheory do not consider in spiral case circumferential plane the heterogeneity of import circumference flow parameter with
The influence in flow field, thus the spiral case performance come out by this Theoretical Design is bad, deteriorates more especially in high back pressure working condition
Substantially.
The volute structure of various centrifugal blowers is also disclosed that in the prior art, such as Patent No. ZL 201110118687.5
Disclosed in the Chinese invention patent of (Authorization Notice No. is the B of CN 102182707)《A kind of centrifugal blower used for range hood and its
Spiral case inlet pressure generation method》, the spiral case includes spiral case top plate, spiral case bottom plate and spiral case coaming plate, the wheel in spiral case coaming plate medial type face
Profile is spiral case inlet pressure, and spiral case inlet pressure is by first straight line DE, the first circular arc line EF, the second circular arc line FG, helix GH, second straight
Line segment HI, which smoothly transits, to be formed by connecting, although after spiral case uses above-mentioned spiral case inlet pressure, being advantageous to improve centrifugal blower air quantity, wind
Pressure, efficiency simultaneously reduce aerodynamic noise, but the volute structure is again without taking into full account in spiral case circumferential plane that import circumference flows
The heterogeneity of parameter and the influence in flow field, and the side-to-side dimensions of spiral case compare larger, influence product design size, generally
Ground, spiral case side-to-side dimensions are required for by local modification or cut off to meet installation requirements, still, thus easily cause to flow
Loss aggravation.
Utility model content
Technical problem to be solved in the utility model is to be directed to above-mentioned state of the art, there is provided before one kind can use spiral case
Size compensates the centrifugal blower volute of flow losses caused by spiral case side-to-side dimensions diminish afterwards.
Technical scheme is used by the utility model solves above-mentioned technical problem：The centrifugal blower volute, including protecgulum,
Bonnet and the ring wall being connected between protecgulum and bonnet, the spiral case inlet pressure of the spiral case include positioned at molded line one end start line AC and
Positioned at the end lines MN of the molded line other end, the start line AC and end lines MN are adjacent to fan outlet, it is characterised in that：Should
Spiral case inlet pressure also includes the first constant helix CD of the angle of flare and tapered the second helix EM of the angle of flare, first spiral shell
Spin line CD is connected with start line AC, and the second helix EM is connected with end lines MN, also, the ring wall is in fan outlet
Outer side edges front and rear width be more than inner side edge front and rear width.
Preferably, the section of the fan outlet is in isosceles trapezoid, and the ring wall is in the outer side edges of fan outlet
The long side of the isosceles trapezoid is formed for long side, ring wall forms the short side of the isosceles trapezoid in the inner side edge of fan outlet.So,
Spiral case ring wall can preferably supplement flow losses caused by spiral case diminishes because of side-to-side dimensions in the change of fore-and-aft direction.
Vortex and loss caused by the Secondary Flow formed in the axial direction in order to avoid impeller outlet air-flow, in the snail
The inside of shell is provided with dividing plate, and the dividing plate is parallel to each other with protecgulum, bonnet.
As a kind of preferred scheme, the D points of the first described helix CD overlap with the second helix EM E points.
So, the first helix CD and the second helix EM are only included between start line AC and end lines MN.
Further preferably, the polar radius R of the first helix CDCDIt is defined as：Its
In, R2For impeller outer diameter, t is impeller excircle and the design gaps on snail tongue top, and t/R2∈ [0.01,0.15], angle of flare α
∈ [3 °, 8 °], θ0For the start angle of the first helix CD D points, and θ0∈ [60 °, 180 °], θ are that the first helix CD takes up an official post
The polar angle variable of meaning point, the polar radius R of the second helix EMEMIt is defined as：
Wherein, R2For impeller outer diameter, t is impeller excircle and the design gaps on snail tongue top, and t/R2∈ [0.01,0.15], variable expansion
Subtended angleα1∈[3°,8°],α2∈ [3 °, 8 °] and α1≥α2,Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the pole of arbitrfary point on the second helix EM
Coordinate angle variables, α1For the angle of flare of D points, α2For the angle of flare of M points,For the second helix EM cornerite.
Further preferably, the ring wall before and after the outer side edges of fan outlet width W and ring wall in fan outlet
Inner side edge front and rear width W0Between meetWherein, S be adjustment factor and
Meet S ∈ [0.7,1.3], W/W0∈(1,1.5]。
As another preferred scheme, the D points of the first helix CD and the second helix EM E points not phase mutual respect
Close, also, D points are located across spiral case central point O horizontal line OH top, and E points are located across spiral case central point O horizontal line
OH lower section.So, the first helix CD, the second helix EM are included between start line AC and end lines MN and positioned at
DE between one helix CD and the second helix EM, the i.e. right side of spiral case are equivalent to having carried out local excision.
Further preferably, the polar radius R of the first helix CDCDIt is defined as：Its
In, R2For impeller outer diameter, t is impeller excircle and the design gaps on snail tongue top, and t/R2∈ [0.01,0.15], angle of flare α
∈ [3 °, 8 °], θ0For the start angle of the first helix CD D points, and θ0∈ [160 °, 180 °), θ is on the first helix CD
The polar angle variable of arbitrfary point, the polar radius R of the second helix EMEMIt is defined as：
Wherein, R2For impeller outer diameter, t is impeller excircle and the design gaps on snail tongue top, and t/R2∈ [0.01,0.15], the variable angle of flareα1∈[3°,8°],α2∈ [3 °, 8 °] and α1≥α2,
Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the polar angle variable of arbitrfary point on the second helix EM,
α1For the angle of flare of E points, α2For the angle of flare of M points,For the second helix EM cornerite.
In order that the influence after the excision of spiral case right side to fan performance is reduced to minimum, the E points and spiral case central point O
Between line OE and the horizontal line OH between angle ω meet 0<ω≤25°.
Further preferably, the ring wall before and after the outer side edges of fan outlet width W and ring wall in fan outlet
Inner side edge front and rear width W0Between meetWherein, S be adjustment factor and
Meet S ∈ [0.7,1.3], W/W0∈(1,1.5]。
Compared with prior art, the utility model has the advantage of：The centrifugal blower volute spiral case inlet pressure also includes expanding
The first constant helix CD of subtended angle and tapered the second helix EM of the angle of flare, and spiral case ring wall is in the outside of fan outlet
The front and rear width on side is more than the front and rear width of inner side edge, so, spiral case side-to-side dimensions is transformed into front and rear chi by Transformed area
In very little change, the fluency that spiral case internal gas flow is collected and passed through, larger lifting maximum static pressure and effective wind rate section are improved
Static pressure, realize and be issued to big spiral case effect in small size, lift Consumer's Experience.
Brief description of the drawings
Fig. 1 is the structural representation of the utility model embodiment one；
Fig. 2 is the spiral case inlet pressure schematic diagram corresponding to the spiral case of the utility model embodiment one；
Fig. 3 is the spiral case inlet pressure schematic diagram corresponding to the spiral case of the utility model embodiment two.
Embodiment
The utility model is described in further detail below in conjunction with accompanying drawing embodiment.
Embodiment one：
As depicted in figs. 1 and 2, using direction shown in arrow F in Fig. 1 as before to the centrifugal blower volute bag in the present embodiment
Protecgulum 1, bonnet 2 and the ring wall 3 being connected between protecgulum and bonnet are included, the spiral case inlet pressure of the spiral case is included positioned at molded line one end
The start line AC and end lines MN positioned at the molded line other end, start line AC are including the straight line AB adjacent to fan outlet 4 and correspondingly
Adjacent to fan outlet 4, the spiral case inlet pressure also includes being connected to start line AC in turn by curve BC in snail tongue position, end lines MN
The first helix CD, trimming DE and the second helix EM between end lines MN.First helix CD D points and the second spiral
Line EM E points are not overlapped, and D points are located across spiral case central point O horizontal line OH top, and E points are located across in spiral case
Heart point O horizontal line OH lower section, also, the angle ω between the line OE and horizontal line OH between E points and spiral case central point O
Meet 0<The angle of flare of the first helix CD in the present embodiment of ω≤25 ° keeps constant, and the second helix EM angle of flare is gradually
Contracting.Specifically, the first helix CD polar radius RCDIt is defined as：Wherein, R2For impeller outer
Footpath, t are the design gaps on impeller excircle and snail tongue top, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0For
The start angle of first helix CD D points, and θ0∈ [160 °, 180 °), θ is the polar coordinates of arbitrfary point on the first helix CD
Angle variables, the second helix EM polar radius REMIt is defined as：Wherein, R2For impeller outer
Footpath, t are the design gaps on impeller excircle and snail tongue top, and t/R2∈ [0.01,0.15], the variable angle of flareα1∈[3°,8°],α2∈ [3 °, 8 °] and α1≥α2,
Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the polar angle variable of arbitrfary point on the second helix EM,
α1For the angle of flare of E points, α2For the angle of flare of M points,For the second helix EM cornerite.By taking the angle of flare of E points in Fig. 2 as an example,
It is described as follows, L1 is tangential on E points perpendicular to OE, L2 and the second helix EM, then the angle α between L1 and L21As volute type
The angle of flare of the line in E points.
In order to compensate flow losses caused by spiral case side-to-side dimensions diminish, the ring wall 3 of the centrifugal blower volute is in blower fan
The front and rear width of the outer side edges of air outlet 4 is more than the front and rear width of inner side edge.And the front and rear width W of above-mentioned outer side edges with it is above-mentioned interior
The front and rear width W of side0Between meetWherein, S is adjustment factor and satisfaction
S ∈ [0.7,1.3], W/W0∈(1,1.5]。
The section of the fan outlet 4 of the present embodiment is in isosceles trapezoid, and ring wall 3 is in the outer side edges of fan outlet 4
Long side forms the long side of the isosceles trapezoid, and ring wall 3 forms the short side of the isosceles trapezoid in the inner side edge of fan outlet 4.Certainly,
The section of fan outlet 4 may not be isosceles trapezoid, such as, can be independent when carrying out variable cross-section compensation in the axial direction
Toward the front side of ring wall or rear side increase size, size, but increased chi can also be increased simultaneously toward the front side of ring wall and rear side
It is very little can be different.
Further, since spiral case axis direction (fore-and-aft direction) increase size to form long and narrow square close to outlet side spiral case
Tee section, impeller outlet air-flow can form Secondary Flow in axis direction, can cause greater loss, therefore, be set in the inside of spiral case
There is the dividing plate 5 for being shunted to spiral case transverse flow channels, and dividing plate 5 is parallel to each other with protecgulum 1, bonnet 2.After dividing plate 5 is set,
Spiral case transverse flow channels can be shunted to avoid the whirlpool and loss that Secondary Flow brings.
Volute air-inlet circumferential asymmetry even property is considered during the centrifugal blower volute Profile Design, by by start line AC with knot
Spiral case inlet pressure between bunch MN is designed to the first helix CD, the tangent line DE being sequentially connected and the second helix EM, the first spiral shell
Spin line CD is equiangular helical spiral, and the second helix EM is the tapered variable angle spiral of the angle of flare, and tangent line DE is equivalent on the right side of spiral case
Portion carries out local excision, so that the side-to-side dimensions of spiral case further reduce, improves spiral case internal gas flow and collects and pass through
Fluency, hence it is evident that improve maximum static pressure and the static pressure of effective wind rate section, realize and be issued to big spiral case effect in small size, together
When reduce aerodynamic noise, improve Consumer's Experience.Also, supplemented by the variable cross-section of spiral case axial direction, it is possible to reduce because
Spiral case side-to-side dimensions diminish and flow losses caused by local excision.
Embodiment two：
As shown in figure 3, the first helix CD D points and the second helix EM E points in the spiral case inlet pressure of the present embodiment
Overlap, i.e. the first helix CD and the second helix EM is joined directly together.
In addition, the first helix CD polar radius RCDIt is defined as：Wherein, R2For leaf
Take turns external diameter, t is the design gaps on impeller excircle and snail tongue top, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °,
8 °], θ0For the start angle of the first helix CD D points, and θ0∈ [60 °, 180 °], θ are arbitrfary point on the first helix CD
Polar angle variable, the second helix EM polar radius REMIt is defined as：Wherein, R2For
Impeller outer diameter, t are the design gaps on impeller excircle and snail tongue top, and t/R2∈ [0.01,0.15], the variable angle of flareα1∈[3°,8°],α2∈ [3 °, 8 °] and α1≥α2,
Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are the polar angle variable of arbitrfary point on the second helix EM,
α1For the angle of flare of D points, α2For the angle of flare of M points,For the second helix EM cornerite.
Similarly, in order to compensate flow losses caused by spiral case side-to-side dimensions diminish, the ring wall 3 of the centrifugal blower volute
Width is more than the front and rear width of inner side edge before and after the outer side edges of fan outlet 4.And the front and rear width W of above-mentioned outer side edges with
The front and rear width W of above-mentioned inner side edge0Between meetWherein, S is adjustment factor
And meet S ∈ [0.7,1.3], W/W0∈(1,1.5]。
Remaining structure of the spiral case of the present embodiment is identical with embodiment one, herein not reinflated description.
It the foregoing is only preferred embodiment of the present utility model, it is noted that for those of ordinary skill in the art
For, under the premise of principle of the present utility model is not departed from, a variety of remodeling or improvement can be carried out to the utility model, these are equal
It is considered as within the scope of protection of the utility model.
Claims (10)
1. a kind of centrifugal blower volute, including protecgulum (1), bonnet (2) and the ring wall (3) being connected between protecgulum and bonnet, should
The spiral case inlet pressure of spiral case includes the start line AC and the end lines MN positioned at the molded line other end positioned at molded line one end, the start line
AC and end lines MN is adjacent to fan outlet (4), it is characterised in that：The spiral case inlet pressure also includes constant first of the angle of flare
The helix CD and angle of flare tapered the second helix EM, the first helix CD are connected with start line AC, second spiral shell
Spin line EM is connected with end lines MN, also, ring wall width before and after the outer side edges of fan outlet is more than inner side edge
Front and rear width.
2. centrifugal blower volute according to claim 1, it is characterised in that：The section of the fan outlet (4) in etc.
Waist is trapezoidal, and the ring wall (3) is in the long side that the outer side edges of fan outlet (4) are that long side forms the isosceles trapezoid, ring wall (3)
The short side of the isosceles trapezoid is formed in the inner side edge of fan outlet (4).
3. centrifugal blower volute according to claim 1, it is characterised in that：Dividing plate (5) is provided with the inside of the spiral case,
The dividing plate (5) is parallel to each other with protecgulum (1), bonnet (2).
4. according to the centrifugal blower volute described in claim 1 or 2 or 3, it is characterised in that：The D of the first described helix CD
The E points of point and the second helix EM overlap.
5. centrifugal blower volute according to claim 4, it is characterised in that：The polar radius R of the first helix CDCDIt is fixed
Justice is：Wherein, R2For impeller outer diameter, t is between the design on impeller excircle and snail tongue top
Gap, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0For the start angle of the first helix CD D points, and θ0∈
[60 °, 180 °], θ be the first helix CD on arbitrfary point polar angle variable, the polar radius R of the second helix EMEM
It is defined as：Wherein, R2For impeller outer diameter, t is impeller excircle and the design on snail tongue top
Gap, and t/R2∈ [0.01,0.15], the variable angle of flareα1∈[3°,
8°],α2∈ [3 °, 8 °] and α1≥α2,Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠ 1, θ are
The polar angle variable of arbitrfary point, α on second helix EM1For the angle of flare of D points, α2For the angle of flare of M points,For second
Helix EM cornerite.
6. centrifugal blower volute according to claim 5, it is characterised in that：The ring wall (3) is in fan outlet
(4) the front and rear width W and ring wall width W before and after the inner side edge of fan outlet of outer side edges0Between meetWherein, S is adjustment factor and meets S ∈ [0.7,1.3], W/W0∈(1,
1.5]。
7. according to the centrifugal blower volute described in claim 1 or 2 or 3, it is characterised in that：The D points of the first helix CD
Do not overlapped with the second helix EM E points, also, D points are located across spiral case central point O horizontal line OH top, E points
It is located across spiral case central point O horizontal line OH lower section.
8. centrifugal blower volute according to claim 7, it is characterised in that：The polar radius R of the first helix CDCDIt is fixed
Justice is：Wherein, R2For impeller outer diameter, t is between the design on impeller excircle and snail tongue top
Gap, and t/R2∈ [0.01,0.15], the angle of flare α ∈ [3 °, 8 °], θ0For the start angle of the first helix CD D points, and θ0∈
[160 °, 180 °), θ be the first helix CD on arbitrfary point polar angle variable, the polar radius of the second helix EM
REMIt is defined as：Wherein, R2For impeller outer diameter, t is impeller excircle and snail tongue top is set
Count gap, and t/R2∈ [0.01,0.15], the variable angle of flareα1∈
[3°,8°],α2∈ [3 °, 8 °] and α1≥α2,Adjustment item s ∈ [- 0.5,0.5], r ∈ [- 5,5] and r ≠
1, θ be the second helix EM on arbitrfary point polar angle variable, α1For the angle of flare of E points, α2For the angle of flare of M points,For
Second helix EM cornerite.
9. centrifugal blower volute according to claim 8, it is characterised in that：Company between the E points and spiral case central point O
Angle ω between line OE and the horizontal line OH meets 0<ω≤25°.
10. centrifugal blower volute according to claim 8, it is characterised in that：The ring wall (3) is in fan outlet
(4) the front and rear width W and ring wall width W before and after the inner side edge of fan outlet of outer side edges0Between meetWherein, S is adjustment factor and meets S ∈ [0.7,1.3], W/W0∈(1,
1.5]。
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ID=61375488
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109469645A (en) * | 2017-05-23 | 2019-03-15 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute |
| CN109973438A (en) * | 2019-04-24 | 2019-07-05 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute |
| CN110145493A (en) * | 2019-04-24 | 2019-08-20 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute for range hood |
| CN110439861A (en) * | 2018-05-04 | 2019-11-12 | 宁波方太厨具有限公司 | A kind of volute structure of centrifugal blower |
| CN111255746A (en) * | 2018-11-30 | 2020-06-09 | 无锡小天鹅电器有限公司 | Volute air duct, fan assembly and clothes dryer |
| CN115788957A (en) * | 2022-11-29 | 2023-03-14 | 广东顺威精密塑料股份有限公司 | Volute with vortex generator and multi-wing centrifugal fan using volute |
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| CN109469645A (en) * | 2017-05-23 | 2019-03-15 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute |
| CN109469645B (en) * | 2017-05-23 | 2023-12-15 | 宁波方太厨具有限公司 | Centrifugal fan spiral case |
| CN110439861A (en) * | 2018-05-04 | 2019-11-12 | 宁波方太厨具有限公司 | A kind of volute structure of centrifugal blower |
| CN111255746A (en) * | 2018-11-30 | 2020-06-09 | 无锡小天鹅电器有限公司 | Volute air duct, fan assembly and clothes dryer |
| CN109973438A (en) * | 2019-04-24 | 2019-07-05 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute |
| CN110145493A (en) * | 2019-04-24 | 2019-08-20 | 宁波方太厨具有限公司 | A kind of centrifugal blower volute for range hood |
| CN109973438B (en) * | 2019-04-24 | 2021-01-19 | 宁波方太厨具有限公司 | Volute of centrifugal fan |
| CN115788957A (en) * | 2022-11-29 | 2023-03-14 | 广东顺威精密塑料股份有限公司 | Volute with vortex generator and multi-wing centrifugal fan using volute |
| CN115788957B (en) * | 2022-11-29 | 2023-05-30 | 广东顺威精密塑料股份有限公司 | Volute with vortex generator and multi-wing centrifugal fan using same |
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| GR01 | Patent grant |